DK151077B - FLUIDUM VALVE VALVE - Google Patents

FLUIDUM VALVE VALVE Download PDF

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Publication number
DK151077B
DK151077B DK535874AA DK535874A DK151077B DK 151077 B DK151077 B DK 151077B DK 535874A A DK535874A A DK 535874AA DK 535874 A DK535874 A DK 535874A DK 151077 B DK151077 B DK 151077B
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DK
Denmark
Prior art keywords
valve
chamber
control
connection
pressure
Prior art date
Application number
DK535874AA
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Danish (da)
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DK151077C (en
DK535874A (en
Inventor
Henning Boerge Lundsgart
Original Assignee
Dansk Ind Syndikat
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Dansk Ind Syndikat filed Critical Dansk Ind Syndikat
Priority to DK535874A priority Critical patent/DK151077C/en
Priority to GB3963875A priority patent/GB1477565A/en
Priority to DE2543466A priority patent/DE2543466C3/en
Priority to CA236,714A priority patent/CA1011621A/en
Priority to US05/618,016 priority patent/US3981478A/en
Priority to BE160566A priority patent/BE834039A/en
Priority to ZA00756204A priority patent/ZA756204B/en
Priority to CH1284575A priority patent/CH588656A5/xx
Priority to SE7511206A priority patent/SE414423B/en
Priority to CS756788A priority patent/CS212750B2/en
Priority to FR7530762A priority patent/FR2287634A1/en
Priority to NL7511871.A priority patent/NL157700B/en
Priority to DD188771A priority patent/DD121675A5/xx
Priority to JP12138675A priority patent/JPS5517271B2/ja
Priority to PL1975183890A priority patent/PL112398B1/en
Priority to SU752178150A priority patent/SU776574A3/en
Priority to IT9581/75A priority patent/IT1049117B/en
Priority to ES441716A priority patent/ES441716A1/en
Publication of DK535874A publication Critical patent/DK535874A/en
Publication of DK151077B publication Critical patent/DK151077B/en
Application granted granted Critical
Publication of DK151077C publication Critical patent/DK151077C/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
    • F16K31/363—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor the fluid acting on a piston

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Servomotors (AREA)

Description

151077 i151077 i

Opfindelsen angår en fluidumstyret ventil af den i kravets indledning angivne art.The invention relates to a fluid controlled valve of the kind specified in the preamble of the claim.

Fra DE-fremlæggelsesskrift nr. 2.224.576 kendes en 5 fluidumstyret ventil af denne art. I denne kendte ventil er to af tilslutningerne på den som trevejs-tostillings-kontraventil udformede hjælpeventil forbundet med det første henholdsvis det andet ventilkammer. Den tredje tilslutning er gennem en kanal forbundet med en til-10 slutning på tostillings-omstyringsventilen. Denne ventil har to yderligere tilslutninger, hvoraf den ene er forbundet med styrekammeret og den anden med et område med lavt fluidumtryk. Når der foreligger en trykforskel mellem det første og det andet ventilkammer, forbinder hjælpe-15 ventilen automatisk det ventilkammer, hvori det højeste tryk hersker - d.v.s. tilgangskammeret - med den tredje tilslutning og gennem kanalen med den ene tilslutning på omstyringsventi1en.From DE Patent Specification No. 2,224,576 a fluid controlled valve of this kind is known. In this known valve, two of the connections on the auxiliary valve designed as a three-way two-position check valve are connected to the first and second valve chambers respectively. The third connection is connected through a duct to a connection of the two-position control valve. This valve has two additional connections, one connected to the control chamber and the other to a region of low fluid pressure. When there is a pressure difference between the first and second valve chambers, the auxiliary valve automatically connects to the valve chamber in which the highest pressure prevails - i.e. the inlet chamber - with the third connection and through the duct with one connection on the control valve.

Dersom omstyringsventilen skiftes til sin ene endestil-20 ling, forbindes ventilkammeret med det højeste tryk - d.v.s. tilgangskammeret - gennem hjælpeventilen med kanalen, og gennem kanalen med styrekammeret, hvorved dette kammer påvirkes af det højeste tryk. Derved holdes hovedventilen i lukkestillingen. Dersom omstyringsventilen 25 skiftes til sin anden endestilling, afspærres styrekammeret fra den tilslutning på omstyringsventilen, der er forbundet med kanalen, og forbindes med et område med lavt fluidumtryk. Som følge heraf aflastes trykket i styre-kammeret, og hovedventilen åbnes af trykket i tilgangs-30 kammeret.If the control valve is switched to its one end position, the valve chamber is connected to the highest pressure - i.e. the inlet chamber - through the auxiliary valve with the duct, and through the duct with the control chamber, whereby this chamber is affected by the highest pressure. This keeps the main valve in the closing position. If the control valve 25 is switched to its second end position, the control chamber is shut off from the connection of the control valve connected to the duct and connected to a region of low fluid pressure. As a result, the pressure in the control chamber is relieved and the main valve is opened by the pressure in the inlet chamber.

I denne kendte ventil medfører skiftningen af omstyringsventilen fra den ene endestilling til den anden også en trykændring i styrekammeret. Derved vendes retningen af resultantkraften af de på begge sider af trinstemplet 151077 2 udøvede fluidiumtryk, hvorved ventilen åbnes eller lukkes.In this known valve, the change of the control valve from one end position to the other also causes a pressure change in the control chamber. Thereby the direction of the resultant force is reversed by the fluid pressure exerted on both sides of the piston 151077 2, whereby the valve is opened or closed.

Denne funktion er uafhængig af strømningsretningen gennem ventilhuset. Skiftningen af ventilen mellem den åbne og 5 lukkede stilling sker imidlertid ret langsomt, eftersom styrekammerets fulde slagvolumen skal strømme gennem omstyringsventilen. Dette nødvendiggør anvendelsen af en tilsvarende stor omstyringsventil for at sikre en høj gennemstrømningshastighed. Anvendelsen af en stor ventil 10 medfører imidlertid høje omkostninger, idet styreorganer til opnåelse af korte skifte- og reaktionstider er kostbare.This function is independent of the flow direction through the valve body. However, the switching of the valve between the open and closed positions occurs rather slowly, since the full stroke volume of the control chamber must flow through the control valve. This necessitates the use of a correspondingly large bypass valve to ensure a high flow rate. However, the use of a large valve 10 entails high costs, as control means for obtaining short switching and reaction times are expensive.

Det er på baggrund heraf opfindelsens formål at anvise udformningen af en ventil af den indledningsvis nævnte 15 art, der har en meget kort reaktionstid og kan fremstilles med lave omkostninger.In view of the above, it is the object of the invention to provide the design of a valve of the type mentioned initially, which has a very short reaction time and can be manufactured at low cost.

Det angivne formål opnås ved en ventil, som ifølge opfindelsen tillige udviser de i kravets kendetegnende del angivne træk. Herved opnås, at omstyringsventilen kun 20 tjener til omstyring af hjælpeventilen, d.v.s. at den kun tjener til under' selve skifteforløbet at levere en tilstrækkelig mængde trykfluidum til at skifte hjælpeventilen mellem dennes to endestillinger. Denne tryk-fluidummængde er ved en hovedventil af givne dimensioner 25 og et givet stempelslagvolumen væsentligt mindre end styrekammerets slagvolumen, som i den ovenfor omtalte kendte ventil skal strømme gennem omstyringsventilen ind i eller ud af styrekammeret, hver gang hovedventilen skal åbnes eller lukkes. Som følge heraf kan omstyrings-30 ventilens skifte- eller reaktionstid gøres særdeles kort, og takket være dens mindre dimensioner er ventilen også mindre kostbar. Skifte- og reaktionstiden for hjælpeventilen, der skal være udført i noget større dimensioner, kan på enkel måde holdes kort ved passende indret-35 ning af trykfluidum-drivorganerne, hvorfor også hoved- 151077 3 ventilens skifte- og reaktionstid kan gøres kort. Den korte reaktionstid er navnlig af betydning i fluidum-styrede automatiserede anlæg, hvori en række arbejds-5 forløb skal udføres i rask rækkefølge, især i de tilfælde, hvor hvert forløbs start styres direkte af afslutningen af det foregående forløb.The stated object is achieved by a valve which, according to the invention, also exhibits the features specified in the characterizing part of the claim. Hereby it is achieved that the bypass valve serves only 20 to bypass the auxiliary valve, i.e. that it only serves to supply, during the actual switching process, a sufficient amount of pressure fluid to switch the auxiliary valve between its two end positions. This amount of pressurized fluid at a main valve of given dimensions 25 and a given piston stroke volume is substantially smaller than the stroke volume of the control chamber, which in the above-mentioned known valve must flow through the control valve into or out of the control chamber every time the main valve is to be opened or closed. As a result, the switching or reaction time of the control valve can be made extremely short, and thanks to its smaller dimensions, the valve is also less expensive. The auxiliary valve changeover and reaction time, which must be made in somewhat larger dimensions, can be easily kept short by appropriately adjusting the pressure fluid drive means, so that the main valve changeover and reaction time can also be shortened. The short reaction time is especially important in fluid-controlled automated plants, in which a series of work processes must be performed in rapid succession, especially in cases where the start of each course is controlled directly by the end of the previous course.

Opfindelsen forklares i det følgende nærmere under henvisning til den skematiske tegning, hvor fig. 1-3 viser 10 et udførelseseksempel på en ventil ifølge opfindelsen med dens komponenter i tre forskellige stillinger.The invention is explained in more detail below with reference to the schematic drawing, in which fig. 1-3 show an embodiment of a valve according to the invention with its components in three different positions.

Den på tegningen anskueliggjorte ventil omfatter et hus 1 med et aksialt forskydeligt ventillegeme 2, der ved sin ene ende, til højre i tegningens figurer, samvirker med et 15 ventilsæde 3 i huset 1. I sin modsatte ende er ventillegemet 2 udformet som et stempel 4, der passer tæt i en cylindrisk boring i ventilhuset. Mellem stemplet 4 og sædet 3 er der dannet et første ventilkammer 5, og et andet ventilkammer 6 findes til højre for sædet 3. Mellem 20 stemplet 4 og ventilhuset l’s lukkede ende afgrænses et styrekammer 7. Ventilhusets to kamre 5 og 6 er bestemt for tilslutning til en ikke vist fluidumledning, hvis gennemstrømning styres ved hjælp af ventilen, og som det vil blive forklaret mere detaljeret nedenfor, kan strømnings-25 retningen i den tilsluttede ledning være vilkårlig. Som antydet med pile er ventilkammeret 5 tilgangskammer for ventilen i fig. 1 og 2, medens det i fig. 3 er afgangskammer .The valve illustrated in the drawing comprises a housing 1 with an axially displaceable valve body 2, which at one end, on the right in the drawings, cooperates with a valve seat 3 in the housing 1. At its opposite end, the valve body 2 is formed as a piston 4. that fits tightly in a cylindrical bore in the valve body. A first valve chamber 5 is formed between the piston 4 and the seat 3 and a second valve chamber 6 is located to the right of the seat 3. A control chamber 7. The two chambers 5 and 6 of the valve housing are delimited between the piston 4 and the closed end of the valve housing 1. to a fluid line not shown, the flow of which is controlled by the valve, and as will be explained in more detail below, the flow direction in the connected line may be arbitrary. As indicated by arrows, the valve chamber 5 is the access chamber for the valve of FIG. 1 and 2, while in FIG. 3 is a departure chamber.

En magnetisk aktiveret og fjederbelastet omstyringsventil 30 8 med to stillinger har fire porte, af hvilke de to gennem ledninger henholdsvis 9 og 10 er sluttet til hver sit af ventilkamrene 5 og 6. De to andre porte er gennem ledninger 11 og 12 sluttet til hver sin ende af en som glider udformet tostillings-trevejs-hjælpeventil 13, som har to 151077 4 tilgangsporte, der gennem grenledninger 14 og 15 er sluttet til ledningerne henholdsvis 9 og 10, samt en afgangsport, der gennem en ledning 16 er sluttet til ventilhuset 5 l's styrekammer 7. I dette kammer virker yderligere en trykfjeder 17, som påvirker ventillegemet 2 via det dermed fast forbundne trinstempel 4 i retning mod den i fig. 1 viste lukkede stilling.A magnetically actuated and spring-loaded two-position control valve 30 8 has four ports, the two of which are connected through wires 9 and 10 respectively to valve chambers 5 and 6. The other two ports are connected to wires 11 and 12 respectively. end of a sliding two-position three-way auxiliary valve 13 having two inlet ports connected through branch lines 14 and 15 to the lines 9 and 10 respectively, and an outlet port connected through a line 16 to the valve housing 5 l. control chamber 7. In this chamber, a further compression spring 17 acts to actuate the valve body 2 via the associated piston 4 connected in the direction towards the one shown in FIG. 1 closed position.

Fig. 1 viser hovedventilen 1,2 og de tilhørende styre-10 ventiler 8 og 13 i den stilling, hvor omstyringsventilen 8 er stillet til lukning af hovedventilen, og hvor ventilkammeret 5 er tilgangskammer for ventilhuset 1. Som følge heraf er trykket i ventilkammeret 5 højere end i ventil-kammeret 6, og da disse tryk gennem ledningerne hen-15 holdsvis 9, 12 og 10, 11 påvirker hjælpeventilen 13's glider, virker også det relativt høje tilgangstryk fra ventilkammeret 5 gennem ledningerne 9, 14 og 16 i styrekammeret 7. Ventillegemet 2 og stemplet 4 er således, foruden af fjederen 17, påvirket af en mod højre virkende 20 resulterende kraft fra fluidumtrykkene, således at ventillegemet holdes i anlæg mod sædet 3.FIG. 1 shows the main valve 1,2 and the associated control valves 8 and 13 in the position where the control valve 8 is positioned to close the main valve and where the valve chamber 5 is the inlet chamber for the valve housing 1. As a result, the pressure in the valve chamber 5 is higher than in the valve chamber 6, and as these pressures through the conduits 15, 9, 12 and 10, 11 respectively affect the slides of the auxiliary valve 13, the relatively high inlet pressure from the valve chamber 5 also acts through the conduits 9, 14 and 16 in the control chamber 7. The valve body 2 and the piston 4 is thus, in addition to the spring 17, influenced by a force acting on the right 20 from the fluid pressures, so that the valve body is held against the seat 3.

Hvis der i denne situation gives ordre til åbning af hovedventilen, dvs. at omstyringsventilen 8's magnetspole sættes under spænding, skifter denne ventil om til den i 25 fig. 2 viste stilling. Herved ombyttes forbindelserne mellem ledningerne 9, 10 og 11, 12, således at hjælpe ventilen 13's glider nu påvirkes af en modsat rettet kraft, som forskyder den til sin modsatte yderstilling. Forbindelsen mellem ledningerne 14 og 16 afbrydes, og 30 sidstnævnte ledning forbindes i stedet med ledningen 15 og gennem ledningen 10 med ventilkammeret 6, hvori det relativt lave tryk på hovedventilen 1,2's nedstrømsside råder.If in this situation orders for opening the main valve, ie. that the solenoid coil 8 of the control valve 8 is energized, this valve switches to the one shown in FIG. 2. Hereby, the connections between lines 9, 10 and 11, 12 are exchanged, so that the slider of the valve 13 is now affected by an opposite directed force which displaces it to its opposite extreme position. The connection between conduits 14 and 16 is disconnected and the latter conduit is instead connected to conduit 15 and through conduit 10 to valve chamber 6, wherein the relatively low pressure on the downstream side of main valve 1,2 prevails.

Det heraf følgende trykfald i styrekammeret 7 bevirker, at resultanten af fluidumkræfterne på ventillegemet 2 og 35 stemplet 4 nu skifter retning, og under forudsætning af, 151077 5 at resultanten kan overvinde fjederen 17's kraft, forskydes stemplet mod venstre og åbner derved for gennemstrømningen gennem ventilen.The resultant pressure drop in the control chamber 7 causes the resultant of the fluid forces on the valve body 2 and the piston 4 to now change direction, and assuming that the resultant can overcome the force of the spring 17, the piston is shifted to the left, thereby opening the flow through the valve. .

5 Fig. 3 anskueliggør den situation, hvor omstyringsventilen 8 stadig har ordre til at holde hovedventilen 1,2 åben, men hvor strømningsretningen gennem sidstnævnte er den modsatte af den i fig. 2 viste. Som følge heraf er trykket nu højere i ventilkammeret 6 end i ventilkammeret 5, og da 10 forbindelsen mellem disse to ventilkamre og de to ender af ventilen 13's glider er uændret fra det i fig. 2 viste, påvirkes glideren nu i modsat retning, således at den indtager samme stilling som i fig. 1. Ventilhuset l's styrekammer 7 er derfor nu gennem ledningerne 16 og 14 15 sluttet til ledningen 9 og dermed til ventilkammeret 5, hvilket indebærer, at trykket i styrekammeret 7 stadig er lig med trykket på hovedventilen 1,2's nedstrømsside, og de på stemplet 4 og ventillegemet 2 virkende kræfter er derfor stadig rettet mod venstre, således at ventilen 20 forbliver åben.FIG. 3 illustrates the situation where the bypass valve 8 still has the order to keep the main valve 1,2 open, but where the flow direction through the latter is the opposite of that of FIG. 2. As a result, the pressure is now higher in the valve chamber 6 than in the valve chamber 5, and since the connection between these two valve chambers and the two ends of the valve 13 slides is unchanged from that of FIG. 2, the slider is now actuated in the opposite direction so that it occupies the same position as in FIG. Therefore, the control chamber 7 of the valve body 1 is now connected through the conduits 16 and 14 to the conduit 9 and thus to the valve chamber 5, which means that the pressure in the control chamber 7 is still equal to the pressure on the downstream side of the main valve 1,2 and those on the piston 4. and the forces acting by the valve body 2 are therefore still directed to the left so that the valve 20 remains open.

Det vil ses, at dersom det ringformede areal af stemplet 4, som vender mod ventilkammeret 5, og arealet af ventillegemet 2’s endeflade, som vender mod ventilkammeret 6, hver for sig er lig med halvdelen af styrekammeret 7' s 25 tværsnitsareal, er de fluidumkræfter, som påvirker stemplet og ventillegemet mod venstre, uafhængige af fluidumets gennemstrømningsretning. Ved voksende strømningshastighed vokser det på ventillegemet virkende dynamiske tryk, hvorved ventillegemet trykkes mod venstre, 30 og gennemstrømningsarealet mellem dette og sædet vokser, medens arealet omvendt aftager ved faldende strømningsmængde. Ved passende konstruktion af ventilen kan gennemstrømningsarealet indstille sig efter mængdestrømmen på en sådan måde, at trykfaldet over sædet 35 er stort set uafhængigt af mængdestrømmen. Hvis ventilenIt will be seen that if the annular area of the piston 4 facing the valve chamber 5 and the area of the end surface of the valve body 2 facing the valve chamber 6 is equal to half the cross-sectional area of the control chamber 7, they are fluid forces. , which affects the piston and valve body to the left, independent of the flow direction of the fluid. At increasing flow rate, the dynamic pressure acting on the valve body grows, whereby the valve body is pressed to the left, 30 and the flow area between it and the seat increases, while the area inversely decreases with decreasing flow rate. By appropriate construction of the valve, the flow area can adjust to the flow rate in such a way that the pressure drop across the seat 35 is substantially independent of the flow rate. If the valve

Claims (2)

151077 anvendes i et hydraulisk system med variabel pumpe, kan man opnå en meget hurtig omstyring af ventilen ved at kombinere en ordre til henholdsvis lukning eller åbning af 5 ventilen med henholdsvis en formindskelse eller forøgelse af pumpens leveringsmængde, hvorved ændringen i leverings-mængden understøtter den ønskede forskydning af ventil-legemet. I tilfælde af strømsvigt til styrekredsløbet sørger omstyringsventilen 8's fjeder for, at ventilhusets 10 styrekammer 7 altid uanset trykforholdene i det tilsluttede system er sluttet til ventilhusets tilgangstryk, hvorved ventilen enten lukker eller fastholdes i sin tidligere lukkede stilling. For fuldstændigheds skyld skal det nævnes, at det ovenfor 15 beskrevne styringssystem også med passende konstruktive ændringer vil kunne anvendes ved ventiler, hvor åbningen -i stedet for som ovenfor beskrevet lukningen - foregår ved tilslutning af ventilhusets styrekammer til det relativt høje tryk på opstrømssiden.151077 is used in a hydraulic system with a variable pump, a very quick control of the valve can be achieved by combining an order for closing or opening the valve, respectively, with a reduction or increase in the delivery quantity of the pump, thereby supporting the change in the delivery quantity. desired displacement of the valve body. In the event of a power failure to the control circuit, the spring of the control valve 8 ensures that, regardless of the pressure conditions in the connected system, the control chamber 7 of the valve housing 10 is always connected to the valve pressure of the valve housing, whereby the valve either closes or is held in its previously closed position. For the sake of completeness, it should be mentioned that the control system described above can also be used with appropriate structural changes for valves, where the opening - instead of the closure described above - takes place by connecting the valve chamber control chamber to the relatively high pressure on the upstream side. 20 PATENTKRAV Fluidumstyret ventil af den art, der omfatter a) et ventilhus (1) med al) et første (5) og et andet (6) ventilkammer med et derimellem beliggende ventilsæde (3), 25 a2) et i ventilhuset (1) forskydeligt ventillegeme (2), der er indrettet til at samvirke med ventilsædet (3) og er fast forbundet med et trinstempel (4), hvis ene stempeloverflade påvirkes af fluidumtrykket i det første ventilkammer (5) og hvis anden og større 30 stempeloverflade påvirkes af fluidumtrykket i et i ventilhuset (1) udformet styrekammer (7), b) en tostillings-omstyringsventil (8), som kan betjenes af et eksternt kommandosignal for efter valg at skifte ventillegemet (2) mellem den åbne og lukkede 35 stilling, og 151077 σ) en trevejs-tostillings-hjælpeventil (13), som efter valg kan forbinde styrekammeret (7) med det første (5) eller det andet (6) ventilkammer, 5 kendetegnet ved, d) at tostillings-omstyringsventilen (8) er en fire-vejs-ventil og omfatter dl) en første tilslutning, der er forbundet med det første ventilkammer (5), 10 d2) en anden tilslutning, der er forbundet med det andet ventilkammer (6), d3) en tredje tilslutning, der er forbundet med et skifteorgan til at føre hjælpeventilen (13) til den ene endestilling, hvori den forbinder styrekammeret (7) 15 med det første ventilkammer (5), og d4) en fjerde tilslutning, der er forbundet med et skifteorgan til at føre hjælpeventilen (13) til den anden endestilling, hvori den forbinder styrekammeret (7) med det andet ventilkammer (6), samt 20 e) at tostillings-omstyringsventilen (8) i sin ene stilling forbinder den første tilslutning med den tredje og den anden tilslutning med den fjerde, og i sin anden stilling forbinder den første tilslutning med den fjerde og den anden tilslutning med den tredje.A patent valve Fluid controlled valve of the type comprising a) a valve housing (1) with all) a first (5) and a second (6) valve chamber with an intermediate valve seat (3), 25 a2) one in the valve housing (1) displaceable valve body (2) adapted to cooperate with the valve seat (3) and is firmly connected to a step piston (4) whose one piston surface is affected by the fluid pressure in the first valve chamber (5) and whose second and larger piston surfaces are affected by the fluid pressure in a control chamber (7) formed in the valve body (1), b) a two-position control valve (8) operable by an external command signal to selectively switch the valve body (2) between the open and closed positions, and 151077 σ) a three-way two-position auxiliary valve (13) which can optionally connect the control chamber (7) to the first (5) or the second (6) valve chamber, 5, characterized in, d) that the two-position control valve (8) is a four-way valve and includes dl) a first connection which e r is connected to the first valve chamber (5), 10 d2) a second connection connected to the second valve chamber (6), d3) a third connection connected to a switching means for passing the auxiliary valve (13) to the one an end position in which it connects the control chamber (7) 15 to the first valve chamber (5), and d4) a fourth connection connected by a switching means to pass the auxiliary valve (13) to the second end position in which it connects the control chamber (7) with the second valve chamber (6), and e) the two-position control valve (8) in its one position connects the first connection with the third and the second connection with the fourth, and in its second position the first connection connects to the fourth and the second connection with the third.
DK535874A 1974-10-11 1974-10-11 FLUIDUM VALVE VALVE DK151077C (en)

Priority Applications (18)

Application Number Priority Date Filing Date Title
DK535874A DK151077C (en) 1974-10-11 1974-10-11 FLUIDUM VALVE VALVE
GB3963875A GB1477565A (en) 1974-10-11 1975-09-26 Fluid flow control valves
DE2543466A DE2543466C3 (en) 1974-10-11 1975-09-29 Fluid controlled valve
CA236,714A CA1011621A (en) 1974-10-11 1975-09-30 Fluid flow control valve
US05/618,016 US3981478A (en) 1974-10-11 1975-09-30 Fluid flow control valve
BE160566A BE834039A (en) 1974-10-11 1975-09-30 FLUID FLOW CONTROL VALVE
ZA00756204A ZA756204B (en) 1974-10-11 1975-09-30 A fluid flow controlvalve
CH1284575A CH588656A5 (en) 1974-10-11 1975-10-03
SE7511206A SE414423B (en) 1974-10-11 1975-10-07 FLUIDUM CONTROLLED VALVE WITH A VALVE SOCKET CONNECTING THE VALVE ORGAN LINELY INSERTABLE IN THE VALVE HOUSE AND CONNECTED TO A DIFFERENTIAL PISTON
CS756788A CS212750B2 (en) 1974-10-11 1975-10-07 Throughflow regulating valve
FR7530762A FR2287634A1 (en) 1974-10-11 1975-10-08 FLUID FLOW CONTROL VALVE ACTUATED BY THE FLUID ITSELF
DD188771A DD121675A5 (en) 1974-10-11 1975-10-09
JP12138675A JPS5517271B2 (en) 1974-10-11 1975-10-09
PL1975183890A PL112398B1 (en) 1974-10-11 1975-10-09 Control valve especially for controlling the flow of a liquid
NL7511871.A NL157700B (en) 1974-10-11 1975-10-09 FLUID FLOW CONTROL VALVE.
SU752178150A SU776574A3 (en) 1974-10-11 1975-10-10 Valve switch
IT9581/75A IT1049117B (en) 1974-10-11 1975-10-10 FLOW RATE CONTROL VALVE
ES441716A ES441716A1 (en) 1974-10-11 1975-10-10 Fluid flow control valve

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DK535874A DK151077C (en) 1974-10-11 1974-10-11 FLUIDUM VALVE VALVE
DK535874 1974-10-11

Publications (3)

Publication Number Publication Date
DK535874A DK535874A (en) 1976-04-12
DK151077B true DK151077B (en) 1987-10-26
DK151077C DK151077C (en) 1988-04-05

Family

ID=8141792

Family Applications (1)

Application Number Title Priority Date Filing Date
DK535874A DK151077C (en) 1974-10-11 1974-10-11 FLUIDUM VALVE VALVE

Country Status (18)

Country Link
US (1) US3981478A (en)
JP (1) JPS5517271B2 (en)
BE (1) BE834039A (en)
CA (1) CA1011621A (en)
CH (1) CH588656A5 (en)
CS (1) CS212750B2 (en)
DD (1) DD121675A5 (en)
DE (1) DE2543466C3 (en)
DK (1) DK151077C (en)
ES (1) ES441716A1 (en)
FR (1) FR2287634A1 (en)
GB (1) GB1477565A (en)
IT (1) IT1049117B (en)
NL (1) NL157700B (en)
PL (1) PL112398B1 (en)
SE (1) SE414423B (en)
SU (1) SU776574A3 (en)
ZA (1) ZA756204B (en)

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Also Published As

Publication number Publication date
BE834039A (en) 1976-01-16
JPS5164633A (en) 1976-06-04
CS212750B2 (en) 1982-03-26
DK151077C (en) 1988-04-05
DK535874A (en) 1976-04-12
FR2287634B1 (en) 1977-12-16
SE414423B (en) 1980-07-28
IT1049117B (en) 1981-01-20
SE7511206L (en) 1976-04-12
FR2287634A1 (en) 1976-05-07
NL157700B (en) 1978-08-15
PL112398B1 (en) 1980-10-31
NL7511871A (en) 1976-04-13
US3981478A (en) 1976-09-21
CA1011621A (en) 1977-06-07
DE2543466A1 (en) 1976-04-15
ZA756204B (en) 1976-09-29
DE2543466B2 (en) 1978-08-31
CH588656A5 (en) 1977-06-15
GB1477565A (en) 1977-06-22
SU776574A3 (en) 1980-10-30
DE2543466C3 (en) 1979-04-26
JPS5517271B2 (en) 1980-05-10
ES441716A1 (en) 1977-03-16
DD121675A5 (en) 1976-08-12

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